Automatic coil winding machine



f .21, 1941; s, -f 2,26Q,053 r v AUTOMATIC con, WINDING MACHINE Filed Aug. 28, 1940 4 SheeIs -Sheet 1,

Us I.

INVENTOR' STEPHENAPLATT FY I ATTORNEYS 4 Sheet-Sheaf. 3

s. A. P AT-r AUTOMATIC coI LyINnING MACHINE F11ed Aug.j2a, 1940 Oct. 21', 1941.

INVENTOR STEPHEN A.PLATT BY 2 z ATTORNEYS, I

Oct. 21, 1941."

s. A. PLATT 'AUFI'OMATIG COIL WINDING MACHINE Filed Aug. 2s,v 1940 4 Sheets-Sheet '4 INVEN'i'QR STEPHEN APLA'IT BY 2 ATTORNEYS Patented Oct. 21, 1941 UNlTED .AUToMA'rIc'con. wnmma Stephen A. Platt, Nutley, N. J., assignor to Wilbur r B. Driver Company, Newark, N. 1., acorporation of New Jersey Application August 28, 1940,- Serial No. 354,474.

reclaims.- (c1. 153-64) The present invention relates to automatic coil winding machinery, and more particularlyto automatic machinery for manufacturing electrical 'resistance coils. The present application is a continuation in part of my co-pending applica- 5 tion Serial No. 290,397, filed August 9, 1939, now

United States Patent No. 2,227,602, issued Janu-.

ary 7, 1941.

The automatic {production of resistance coils on a quantitative basis requires a machine capable of producing coils of uniform physical and electrical characteristics. The coils produced should be uniformly wound and with small tol? erances have the same electrical resistance ratings for a given length and wire size.

' The importance of uniformity is so great that in some instances, where, for example, the resistance units operate very close to their melting point, the resistance coil units are X-rayed ter under pressure from two freely rotating re silient biasedrolls having high coefflcients of friction, the wire will form acontinuouscoil of uniformly wound andspaced turns having'a uniform pitch determined by the bias of the rolls. The coil turns will move along the mandrel and, after passing from the zone of pressure of the rolls, expand slightly so that the coil will slide freely along. the major length of said mandrel and may then be cut ofi into predetermined lengths afterleaving the mandrel. I

- Accurate automatic cut-off" of predetermined I lengths of coil formed on the machine embodyafter being embedded in magnesium oxide, or the like, to check the spacings of the windings.

Unlike spring wire or steel wire, electrical resistance wire is soft or malleable and is not readily pushed or forced into coil form. It must be pulled or drawn into the desired form. Since the resistance per unit length of the wire depends upon its cross-sectional area, the pulling or drawing operation in winding of the coil must not stretch the wire, and thereby reduce its cross-sectional area and resistance. the coiling machine must not otherwise deform I the wire and thus alter its electrical characteristics.

e the .coil formed by the machine.

Moreover,

The coil winding operation usually winds the adjacent turns of the coil in contact with each uniform spacing between adjacent turns of the coil because lack of uniformity results in a coning the principles disclosed herein and in my aforementioned co-pending applicationis an important' feature for the quantitative rapid production of coils having given desired electrical 'characteristics. To achieve uniformity in rapidly manufactured large quantities of coils, it becomes essential that the cut-off mechanism associated with the coil winding machine operate within very close limits of accuracy. Such cutoff mechanism must also be capable of automatic operation, and, too, must be capable of adjustment and regulation so that differently'sized predetermined coil lengths may be severed from Such cut-off mechanism, too, must be capable of quick adjustment during operation of the machine to compensate for variation in electrical characteristics of the coil wire wound in the machine. It is, therefore, a principal object of this invention to provide novel automatically operated cut-off mechanisms meeting the foregoing requirements.

While the cut-elf mechanisms disclosed herein'are shown applied to the type of coil-winding machine disclosed in my aforesaidco-pending application, it is an object of this invention to provide cut-oifmechanisms applicable to other centration of heat in the. region of the closest 40 coil turns uniformly in such manner as to insure uniform stretching and uniform spacing between individual coil turns when stretched.

The operation of v the machine therein described depends upon the fact that, if coil wire under necessary tension is led to a rotating polished mandrel havinga comparatively-low cotypes of coil winding machines as well.

Another object of the invention comprises the provision of means for cutting off predetermined coil lengths during the winding of the coil With-.

out interfering with the winding operation. This 5 cut-off mechanism must operate intermittently I eilicient of friction, and wound around the lat-'55 so as to sever, in highly accurate manner, coils having substantially uniform predetermined Still another object of the invention is to pro .vide special wear-resistant metering mechanism which serves to operate the cut-off mechanism or resurfacing. f

A further object is toprovide a machine adaptcontrolled cut-off mechanism; and

and which does not require frequent replacement able for winding coils of differently sized wire, and for such coils to have desired different pitches. r

It is another object of this invention to produce a successfully operating machine dependthis invention consists in the construction and arrangement of parts hereinafter described, and then soughtto be defined in the appended claims, reference being had to the accompanying drawings ,forming a part hereof and which shows,

merely for the purpose of illustrative disclosure, preferred embodiments of the invention, it being expressly understood, however, that various changes may be made in practice within-the inventive idea.

In the drawings, in which similar reference characters denote corresponding parts,

Figure 1 is a front elevational view of one form of my novel coil-winding machine;

Fig. 1a is a partial section taken along line la-la of Fig. I viewed in the direction of the arrows;

Fig. 2 isa rear elevation on an enlarged scaleof the said machine shown in Fig. 1;

Fig. 2a is a plan view of the cut-off mechanism of Fig. 2;

Fig. 3 is a vertical section taken along line 3,3 of Fig. 1, viewed in the direction of the arrows, and illustrating the electrically controlled cut-oil mechanism and part of the mechanism for receiving the wound coil;

Fig. 4 is a vertical section taken along line. 4--4 of Fig. 1, viewed in the direction of the arrows; I Figs. 5, 6 and 7 are views on a smaller scale of 7 the electrically controlled cut-off mechanism shown in Fig. 3 and illustrating successive operating positions thereof Fig. 8'is an enlarged detail of the means for controlling the electrical circuit of the cut-ofi means;

Fig. 9 is a rear elevational view of a modified form of machine-in which clutch controlled mechanical cut-oil means are employed;

Fig. 10 is a vertical section taken along line l 0l0 of Fig. 9 and illustrating the cut-off mechanism and part of the guide mechanism for receiving the wound coil;

Fig. 11 is an enlarged detail view of the clutch control means for operating the mechanically Fig. 12 is a detail view of the yoke and clutch scope of the claims without digressing from the horizontally by one of its "ends a windingmandrel l6 upon which the wire is wound into coil form.

Suitable driving means for-rotating the shaft 12 are provided; In the embodiment shown, a

motor 20 has a swinging base 20' adjustably carried on a support rod 2| extending laterally from the machine frame Ill. The rotor shaft 22 of the motor has a cone pulley wheel 23 fixed thereto and whose apex extends oppositely to that of 1 to couple the motor and chuck-bearing axle or shaft I2, so that the motor drives the mandrel I6. I Variability of speed is obtained by shifting the belt from step to step of the cone pulley wheels l3 and 23. A The frame lll forwardly has an upwardly extending vertical flange which has a bore 3| in axial alignment with the shaft II. A tube 32 is fitted into this bore 3| and the free-end of the mandrel extends into, but not through, the entire length of said tube whose diameter is so admeasured as to be only slightly in excess of the diameter of the wire coil wound on the mandrel, as will be presently described.

The rolls 35 and 36 (Fig. 2) of resilient material, such as rubber having a high coefllcient of friction and which co-operate with the mandrel 16 in winding the coil, are supported from the frame III at diametrically Opposite points with respect to said mandrel. These rolls which may drel. Likewise the tworolls are normally-biased with respect to each other and with respect to the mandrel axis and this bias may be varied at will. The mounting of these rolls is indicated in dot-dash line in Fig. 2 and the parts so shown are intended to represent the roll mounting means disclosed in my aforementioned application.

Wire for forming the coils is fed to the mandrel it, from a spool 40. This spool is rotatably and removably carried on a spool spindle 4| trip mechanism for operating the clutch means.

driving belt to be presently described. The opposite' end of the shaft I2 is constructed to receive any standard form of chuck l5, that illustrated being a well-kgow'n key-tightening type. This chuck i5 is ad' -i ied to receive and support suitably supported from the machine frame ID. The wire 42 from said spool is led around a pulley wheel 43, over a second pulley wheel 44,

around a third pulley 45, and around substan-.

tially the major portion of the peripheral surface of a metering wheel 46. All of the wheels are rotatably supported on the front of the frame Ill. The location of the turning center of the metering wheel and the diameter of the said wheel are so arranged that the wire leaves the surface of the metering wheel on the tangent which is perpendicular to the axis of the. mandr'el. The pulley wheels 43, 44 and 45, and particularly pulley wheel 45, are so positioned that the wire must pass from the latter around the major portion of the periphery of the metering mandrel I6 and so positioned that wireleaves the groove 41 thereof on a tangent substantially in the horizontal plane of the lower face of ca'ted with respect to the widths or the rblls I and 88. The wire leaving'the metering wheel surface is passed around a fourth pulley 58- also supported from the bracket 48, around the' groove. 41, and then past a" vertical guide pul ley il'j (Fig, 3), and finally 'be'tween'the bight formed by the mandrel l6 and the lower roll 88,

For eflicient coil'winding,.it is desirable to lubricate only that "surfaceof the ,wire which I feet the said clamping. Therubber ring 1| may comes in direct contact with the surface-of the mandrel, l6. In the embodiment shown,. the

wire surface to be lubricated is the top surface of the wire 42 as it passes from the groove 4l' weight 55 which is suitably carried by the bracket 48. This weight is adapted to press downwardly on the upper end of the lubricating stick.

saidjmandriel l8. The "bracket 48 is carried by I I the frame It and attached thereto as by b lts; the metering wheel h a n iqn II of red d 49,- The groove 41' is substantially centrally -lodia'meter. On the saidreduced portion, a ring' end, the peripheral surface-of med; To this ll, preferably of rubberor of other suitable material, is mounted which is somewhat less in extemal diameter than themaximum external di-L ameter of the wheel 48. A clamping ring 12,

also mounted on said reduced portion 18, serves to clamp the said ring to the annular flange." ofsai'd metering wheel Suitably spaced bolts v 14 extending through said clamping ring, and

rubber ring, and into said flange l3, serve to ef- I to the vertical pulley 5|. To this ehd, a hollow specific metering wheel structure has beensfound.

to be exceedingly wear-resistant. 'In actual The longitudinal axis of th'eilubricating stick is-- arranged tolie substantially perpendicular to the top face of the wire 42 and in the same plane. therewith. Passage of the wire in the groove 41' rotates the worm wheel 41 and consequently causes-rotation of the lubricating stick socket 52 through gear 54. As a result, the lubricating stick 55 rotates as.the wire passes under it and wears down uniformly while lubricating only the one face of the wire 42 which comes into direct contact with the mandrel Hi.

It is necessary to tension the-wire 42 as vit passes from the spool 40 to the mandrel liidur- 'ing-the winding operation. This tensioning is accomplished herein through the agency of the metering wheel 66 (Figs. 1a and 4). The latter is slidably keyed at 60 to the rotatable'shaft 5| borne in a bearing opening 62' in the front face ing opening 62 and of substantially the same diameter as the metering wheel 46. A circular friction disc .or mat 64 is mounted around the shaft 6| betweentheinner face of the metering wheel and the pad surface 63 and pressed betweemth'e two by the compression spring 65 ca ried on the shaft 6|. The-pressure of spring 65 is adjustable through the agency of the washer 86 (Fig. 4) and clamping nut 61,whieh latter threadedly engages the outer threaded end 8| 'of the shaft 6|. This variability of pressure permits adjustment of the frictional resistance between the metering wheel and the frame and consequently permits variation in tension on the wire 42.

Since. the wire passes over theperipheral surface of the metering wheel-at hi h speed during I the coil-winding operation, a special wear-resisting peripheral surface is necessary to eliminate the necessity for frequent replacement of ofl'mechanism whose accuracy, must be maintravels. The friction between the wire 42 and the compressed rubber ring surface in conj nction with the retarding action of the friction pad -64 on the metering wheel surface affords an ad! justable means fortensioning .thewire. ,Thisj practice, hundreds of thousands of miles of wire run over such metering wheels have 'notirequired refacing thereof.

Th'efrotation of the metering wheel caused by the passage of the wire 42 around'it is used to control automatic electrically operated cut-off mechanismwhich serves to cut ofi predetermined lengthsof wound coil. To this end, the metering wheel shaft 6| is provided with a pinion 88. The

I latter meshes with an idler 8| of larger'diameter which is rotatably supported from the frame it) by the spindle 82. v

k A pulley 83 of the variable speed type is rotatably supported on the fram I 0 by the spindle 83'.

This pulley has opposed inclined faces 88' and g 5 85" on separate sections 8.4 and 85 which are adjustably movable toward or away from'each other by means of .a manipulating nut 88 and clamping nut 87. i A' second variable tatably bornegon the spindle 88 carried by the the action of, a compres'sion spring 82 on the eframe iii. .This pulley, too, has oppositely inclined faces" 98 and 9% on separate sections 96 speed type pulley-88 is ro and 8|, one of which is movable toward and away from the otherby the actionof, or against spindle 89 between one of the sections and the frame.

' 83 by a V-shaped belt 93 operating between the opposed faces of the respective pulley sections. The two pulleys and the belt constitute a variable speed drive of the Reeves type in which the rotational speed of the pulley 88 is adjusted A second idler gear Hi3 rotatable with gear |8| on the spindle mesheswith the idler gear 8| which in turn meshes with the gear drivenby rotation of the metering wheel. Thus rotation of the .metering wheel through the gears 88, 8|, I03, IUI and Hill drives the pulley wheels This pulley 88 is coupled to the pulley 84 and 88. Thus, it ispossible to vary the lengths I of the coils cut OH with infinite variation within the limits of the variable speed drive by the electrically-operated cut-oft mechanism now to be described.

The electrically-operated cut-oi! mechanism comprises a reciprocally rotatable knife blade I capable of movement transversely of the axis of the mandrel I8 and the coil .wound thereon:

This knife blade I20 is'adapted to move across the outer end of the tube 32 which has a .cam-

bered end 32' and'to sever the woundcoil whenever'so moved. The knife blad is. removably clamped by clamping plate I2I to one arm I22 of a double armed crank lever I23 which is pivotally supported at I25 from the machine frame flange in such manner that rotation of the crank lever about the pivotal support I25 causes the knife I20 to sweep across the cambered nd 32' of the tube 32 to sever wound coil emerging.

therefrom. The knife blade is adapted tobear reasonably tightly against the cambered end 32? of the tube 32 during the sweeping cutting strok to each other. The locking member also has a across the same to obtain the required shearing of the coil.

Cutting strokes of the knife may be imparted to the knife by electrically controlled apparatus.

tween the tines I32 by a pivot pin I34 extending transversely through the tines and projecting laterally at I 34' and inti a vertical guide s1ot I35 provided in the flange 30. This guide slot serves to insure vertical motion of the plunger and its cross head and limit upward motion thereof.

The link I33 is connected by a pivot pin I38 to two oppositely extending links I38 and I38.

- end I42 of the rod is adapted to extend through an opening I44 in a flange I45 of the frame I0.

The opening I44 is so admeasured as to permit free sliding and angular movement of the rod during operation of the device for a purpose to be presently described. A suitable compression spring I46 serves to urge therod upwardly at all times.

a a Q Q relative to the link I38 and so admeasure din 7 length that when the link I38 andsaid-memher are in parallel relationship, the free end I50 of said locking member extends into the space I31 between links I33 and I38v and bears against the pivot pin I36 maintaining it at theouter end of slot I38 most remote from'pivot member I48. This locking engagement establishes a fixed arm ratio between the linkage members I33, I38 and I38 necessary to effect a severing movement of the blade I20 upon energization of the solenoid I30, in a manner to be presently described.

The locking member has an arcuate slot I5I whose center of curvature is the pivot member I48. A limiting pin I38 on the link I38 extends into this slot and limits relative rotation of the link I38 and locking member I50with' respect lateral flange I50 adjacent the pivot I48.

A snap toggle assembly I52 is attached to this flange forithe purpose of snap swinging of the locking member relative to the link I38to cause engagement and disengagement of the end I50 of the member I50 with the pivot pin I36. This snap toggle assembly comprises a member having a head I52 and longitudinally extending parallel tines I52 The tines areslidable longitudinally of and are rotatable about a fixed pivot pin I54 supported by the flange 30.

- Acompression'spring I55 surrounds the tines between the head I 52' and the pivot-pin I 54 and urges the said head away from the pivot pin I54. The relative spacing and arrangement of the pivots I48 and I54 on the flange 30 is such that counterclockwise rotation of the locking member I50. and the link I38 from the position shown in Fig. 3 moves the toggle head I52 toward the pivot pin I54 and at the same time gives it clockwise rotation about said pivot pin. During this A stop pin I28 suitably supported by the flange A sn'ap locking member I50 is also pivotally supported from the pivot member I48 in spaced relationship relative to the link I38 (Fig. 2a). This locking member is independently rotatable rotation, the spring I55 maintains the locking member I50 in parallel relationship with the link I38 until the forked toggle member I52 rotates past its upper dead center, whereupon the spring I55 thereof exerting leverage action on the flange I50 rotates the locking member in counterclockwise direction with a snapping motion in advance of the link I 38 to the position shown in Fig. 6. Such advanced rotation of the locking member causes the end I50. thereof to disengage the pivot member I36 so that it may slide in the slot I38 toward the inner end of the latter as shown in Fig. '7. Upon return of the parts to the position of Fig. 3,. the toggle action operates in reverse and serves to snap the locking member back into the position shown in this figure.

The arrangement and spacing between the pivot member I48 and pivotal support I25 as well as the dimensional characteristics of the links I 33, I38 and I38 is such that the following action takes place upon energization of the solenoid.

Such energization draws the plunger I3I downwardly into solenoid I30. Such downward movement draws the link I33 downwardly, causing links. I38 and I 38 to assume the horizontal position shown in Fig. 5 at maximum arm ratio. This imparts counterclockwise rotation to the knife-carrying crank lever I23 of such extent that the knife I2 sweeps downwardly across the cambered end 32' of the tube I32 and severs the coil emerging therefrom. After the severing sweep has been accomplished, further downward movement of the plunger I3I continues. This carries or moves the links I38 and I39 to the position shown in Fig. 6. In assuming this position, the link I38 having passed horizontal dead center acts positively to cause clockwise rotation V of the cranklever I23, causin the knife blade I29 to sweep back across the tube into the noncutting p s tion above the tube 32 as shown in Fig. 6. At the same time, the toggle I92 having minal I of the power source, through the wire passed its upper dead center position snaps the locking member I59 in advance of link I39; as shown, and out ofengagement with the pivot I39 so that the latter is free to move in the slot I39".-

Bs soon thereafter as the solenoid I39 isde- 1 energized, the plunger I3I begins to move upwardly as shown in Fig. '1 under action of spring- I42. However, since the pivot pin I39 now can slide freely-in the slot I39 because of disengagement of the locking member I99 frombehind it, it moves toward the right of Fig. '1, so that in the upward stroke of the plunger I3I under actuation of thespr'ing I42, the combined length of links I39 and I39. isinsufllcient to cause any rotaturn, however, of the plunger I3I to the position shown in Fig. 3, the pivot member I39 again moves to the left or outer end of. slot I39 and the toggle again having passed its upp r dead center again snaps the locking member I59 into locking position, i. e., parallel relationship with the link I39'and intoengagement with the pivot I39 so that on down stroke the knife will be swept once across the tube end 32'jin each direction. This actuation of the linkages repeats for 3 eachenergization and de-energization of the solenoid I3 9..

Energization and de-energizat-ion of the solenoid I39 is accomplished by an electric circuit controlledc' throughvrotation of the metering wheel 49.

To this end, a nose flange or cam member I99 is provided on the face of the section 99 of the pulley 99 (Figs. la, 3 and 8). A two pole elec-fl A trio control switch I6I of any standard type and 40 v on the surface of the section 913 in th'p'athof rotation of the nose flange or cam member lot during which period the switch is open. Passage of the flange under the roller its will move the roller and arm and consequently the plunger rod IE2 longitudinally to close the switch circuit.

As soon as the cam flange has cleared the roller, the latter returns under suitable spring actuation into abutting relationship with the surface of the wheel 99 and the switch is reopened.

Atwo-pole mercury switch I19 of standard type serves to supply current from a power' source P to the fieldcoil I39 of the solenoid, the poles HI and I12 of this switch normally in open circuit being in simple electrical series connection with the field coil I39 and power source P-through the wires I13, I13 and I15. The mercury switch is closed by energization of an operating coil I19 which is in simple series circuit with the poles of the control switch I9I and the power source ,P r I through the wires I11, I19 and I19.

Operation of the circuit is asfollows: Closure of the control switch I9I under actuation of the nose or flangeeiiucausespilot current to'flow from one termnial I er the power source P through the wire I11, the pilot switch I9I, the

wire m. the operating coil I19,andthewlre us to the'second terminal 2 of power source. This pilot current flowing in the coil I19 closes the power circuit through the mercury switch I19: permitting power current in flow from one ter- 11:, through the switch poles m, in, through the wire l1l, through the solenoid coil I39,

through the wire I15 to the second terminal 2 of the power source energizing the solenoid coil I39 to operate the solenoid plunger as hereinbefore described. Opening of the pilot switch deenergizes the. mercury switch coil J19 and conseque'ntiy opens the mercury switch tie-energizing the solenoid coil I39' The mercuryswitcn'remains closed only so long as themercury switch coil I19 is energized which, as seen, depends upon t period of engagement of the nose or flange IQQWiththe gqllenllitv-vd m- In the embodiment shown, movement imparted to the nose or flange I99 acts as a trip and the latter is'adapted'to close the pilot switch I9I once for each revolution of the section 99 of pulley wheel 99. Therefore, the speed of rotation of said wheel determines the frequency of actuation or energization of the solenoid I39 and inconsequence the cutting-off action of the blade I29 through the linkage mechanism hereinbefore described. In consequence, the frequency of cuton action can be controlled by changinwgi of'the pulley wheel 93.

hjjg el ectrically controlledcut-oil mechanism operated byiotationnr the metering wheel is .positive in its action and eliminates any irregularity in coil lengths cut off by the blade" I29.

- There is no dangerof double tripping. Simple infinitely variable adjustment of the "variable speed pulley 93, which throughthe belt 93 drives theepulley-9'9and is driven by rotation of the metering wheel 49 through the gears 89,9I, I93,

IM and I99 sen infinitely ariablefl change withir'i'the limits of the variable speed mechanism in the length of coil cut-off by changing the relativepfrequency of cut-ofi action as 5 compared to the speed of coiling of the wire.

The lengths-of coil emerging from the tube 32 which are severed by the blade I29 drop into a .tray or basin 389 carried by the frame below the exit end of said tube. Operation ofthe machine in brief is as follows: Wire 52 from the spool 49 is led over the various pulleys 93, 99, 95, meteringwheel 99, pulley 59 and around grooved? of gear 91 and past pulley iii to the bight between the lower rubber roll 39 and the mandrel I'6. Then the shaft I2 and, consequently, the mandrel I6 are given a few manual rotations to start'the wind on the mandrel. The rolls 35 and are given the desired opposing biases with respect to each other and moved. toward each other until they both press firmly on the wire-windings on the mandrel/ and are clamped in this position. The motor is i then started, causing the mandrel I6. to'rotate at high speed. The coeilicientmf friction between the mandrel and the wire, aided'b thepr'essure of the lower roll 39, is sumcien't to draw'the wire from the spool and. coil, it about themandrel. The bias of the rolls 35 and 39' determines the pitch of the wind and forces the windings to move guide tube, passing of! the mandrelin the tube 32. The lubricant applied by stick 95 to the face of the wire adjacent the face'of the mandrel facilitates the sliding of the coil along the mandrel. At intermittentperiods controlled by the trip cam I60, as hereinbeiore described, the cutoff knife sweeps across the exit end of tube 32 cutting off predetermined lengths of coil which fall into the tray or basin I80 at the time of severance. The adjustable ratio of speed between the coiling speed. of the mandrelandthe I the diameter of the respective rolls on one side of the machine illustrated in Figs. 1-8 inclusive.

The frame 2! forwardly has an upwardly ex tending vertical flange 230 which has a bore 23! in axial alignment with the shaft 2l2. A tube 232 is fitted into this bore 23! and the free end of the mandrel extends into,' but not through, the entire length of said tube whose diameter is so admeasured as to be only slightly in excess'of the diameter of the wire coil wound on the mandrel, as will be presently described.

The rolls 235 and 235 of resilient material. such as rubber having a high coefficient of friction and which cooperate with the mandrel 2l6 in winding the coil, are supported from the frame 2l0 at dia.-.

metrically opposite points with respect to said mandrel. These rolls are supported and operated in the same manner as the rolls 35 and 35 Wire for forming the coils is fed .to the mandrel from a spool 255. This spool' is rotatably and of the respective shoulde @P litate the guiding removably carried on a spool spindle'255 suitably of .the wire at the desired pitchan'gle during the -supportediromflthelmachine frame- .-The wire coiling operation. The shoulder height depends upon the wire size and in cases of very smallsized wire can be eliminated. For the larger wire sizes, howeventhe shoulder is important.

Idler gears l0! and I03 are, in fact, portions of a compound gear supported on the shaft I02. The position of the latter is adjustable in the slot l02a in the frame [0 to permit a changed gear ratio if desired.

The adjustability of the speed of drive of various parts, the adjustability of tension by the metering wheel, as well as the adjustability of the pressure and degreireLbiaseoLthe rolls 35 and 36 makes the machine adaptable for making accurate coils of any. desired predetermined length and of desired different wire sizes.

The material of the mandrel is optional as long, as it is wear-resistant and has a low coeflicient of friction. "Nitrided steel mandrels have been found satisfactory.

In some instances, it may be desirable to rejournal portion of an axle or shaft 2|2 which protrudes from each end of the flange 2| l. One end of the shaft has keyed to it the pulley wheel M3 and the cone pulley wheel 2, each pulley wheel being provided with grooves to receive cor-. respondingly sectioned driving belts to be presently described. The oppositev end of the shaft 212 is constructed to receive any standard form of chuck US, that illustrated being a well-known key-tightening type. This chuck 2l5 is adapted to receive and support horizontally by one of its ends a winding mandrel 2l6 upon which the wire is wound into coil form.

Pulley 2 is suitably driven as by a belt connected with pulley 222- supported on a drive shaft 223 of a mofia r fi'i ot shown). This pulley wheel 222 likewise has grooves similar to those of pulley 2. A driving belt 224 is passedaround the two pulley wheels 222 and 2M and serves to couple the motor axle 223 and the chuck-bearing axle or shaft 2 [2, so that the motor may drive the mandrel 2l6. Variability of speed is obtained by shifting the belt from'step to step of the cone pulley wheels 214 and 222. a

251 from said spool is led around a pulley wheel 258, over a second pulley wheel 259, around a third pulley wheel 260, and around substantially the major portion' of the peripheral surface of a metering wheel 26L All of the wheels are rotatably supported suitably on the front of the frame 2 I 0,. The location of the axis of the metering wheel and the diameter of the latter are so arranged that the wire leaves the surface of the metering. wheel on the tangent which is perpen-' dicular to the axis of the mandrel 2|6. The pulley wheels 258, 259 and 260, and particularly pulley wheel 260, are so positioned that the wire must pass from the latter around the major portion of the periphery of the metering wheel 2H.

Thewiire isledfromthe metering wheel 'to the bight between the mandrel M6 and the biased roll 236 in exactly the same way the wire 42 is fed to the bight between the mandrel l5 and roll 36 of the modification of Figs. 1-8 inclusive, being lubricated on its upper surface in the same way and by the same type of means as that shown in Fig. 3.

It is necessary to tension the wire 251 as it passes from the spool 255 to the mandrel 246 during the: winding operation. This tehsioning is accomplished herein through the agency of the metering wheel '26I in the same manner as that described with respect to the metering wheel 46 of the first modification and illustrated clearly in Fig. 4.

Since the wire passes over the peripheral surface of the metering wheel at high speed during the coil-winding operation a special wear-resisting peripheral surface is necessary to eliminate the necessity for frequent replacement of the metering wheel and consequent readjustment of the machine, particularly because the metering wheel also serves to drive a special cut-off mechanism whose accuracy must be maintained. To this end, the specific metering wheel structure described with respect to the first embodiment is embodied in this modification as well.

The rotation of the metering wheel ZGI caused by the passage of the wire over its prepared periphery is used to drive automatic clutch controlled cut-ofi mechanism which serves to cut off predetermined lengths of wound coil. 3 To this end, the wheel shaft 2! is provided with a pinion 300. The latter meshes with a pinion 3M of larger diameter attached to a pulley wheel structure as the pulley wheel 83 of the first modification. "It has opposedinclined faces on separate sections which are adjustably movable toward or away from each other by means of a manipulating nut. 308 and clamping nut 301.

A second variable speed type pulley 308 is rotatably borne on the spindle 303 carried by the frame 2). This pulley has the same structure as the pulley wheel 88 of the first modification. It has oppositely inclined faces on separate sections, one of which is movable toward and away from the other by the action of, or against the action of,a compression spring (not shown) on the spindle 308 between one of the sections and the frame. This pulley 308 is coupled to the pulley 302 by a belt 313 operating between the opposed faces of the respective pulley sections. The two pulleys and the belt constitute a variable speed drive of the Reeves type in which the'rotationalspeed of the pulley 308' is adjusted by the relative adjustment of the opposing faces of the pulley 302. Thus, it is possible to vary the lengths of the coils cut off by the mechanism now to be described.

The cut-ofi mechanism comprises a reciprocally movable knife blade 320 movable transversely of the axis of the mandrel H8 and the coil wound thereon. This knife blade 320 is adapted to move across the outer end of the tube 232 and sever the wound coil whenever so moved. The knife blade is removably attached at 32l to the connecting rod 323. This connecting rod is provided with a longitudinal slot 324 and a headed guide pin 325, engageable in the vertical arm 230 which serves to guide the vertical movement ofthe connecting rod. The latter at its lower end has a bearing 328. An eccentric 321 integrally formed with a clutch member 328 opcrates in the bearing and serves upon rotation to reciprocate the connecting rod and the blade carried thereby.

The clutch member 328 is rotatably borne and slidable longitudinally on a rotaryshaft 328 suitably journalled in bearings 330 in the frame 2"]. This shaft extends parallelly to shaft 212 and at one, end has a driving pulley 33l. Belting 332 connects this driving pulley with the pulley M3 on shaft 212 so that when the latter is driven, the shaft 329 is likewise driven. In the embodiment shown, the pulley ratio of the diameters of pulleys 2l3 and 33I is such that shaft 328 is driven at a lower speed than shaft H2. The opposite end of shaft 323 has a collar 335 fixed thereto. This collar has two diametrically arranged, axially extending, engaging pins 338, one or the other of which is adapted to engage an oppositely extending pin 331 on the eccentric 321 when the latter andthe clutch member 328 are moved into one position on the shaft 328, thereby serving to drive the eccentric and reciprocate the connecting rod. In another position of the eccentric 321 and clutch member 328- on the clutch member 328 has an annular yoke groove 340. A U-shaped yoke 3 is pivotally supported on a'spindle 342 attached to the frame 2l0 and extending transversely of the shaft328 so that the cam follower 380 clears the shoulder 348 and,

the yoke 34| swings longitudinally of said shaft. The yoke has oppositely extending lugs 344 which permanently engage in the yoke groove 340.

When the yoke is swung about its spindle 342, I

the lugs in the groove 340 serve to shift the clutch member 328 longitudinally on the shaft 328.

The clutch member 328 (Fig. 11) has a single-.

turn, helical cam groove 348 in its peripheral face whose beginning and end are connected by a longitudinally extending passageway 348' which serves to define a shoulder 348 at the exit end of the cam groove and adjacent its entry end.

A cam groove follower 383 of substantially square cross section is suitably supported in vertical direction at 351 from the frame 210. The

lower end 380 .of the follower is adapted'to :engage in the cam groove 348 and normally to abut the shoulder 348 at the exit end of said groove. While so positioned, the clutch member is locked against rotation and the pin 331 is clear of the pins 338. In the embodiment shown, a shift of a the clutch member 328 to the left will cause the resilient member 383 serves to urge said lever against the forward stop pin in the directionof rotation of the pulley section 3I0.

The yoke 34l has a lug 310 projecting laterally into the path of travel of the trip lever 380. As the lever moves upon rotation with the pulley section 3l0,'its free end engages the lug 310 causing the said lever to move back against the rear stop pin 382 whereupon said lever rotates the yoke 341 and slides. the clutch to the left until enters the start of cam groove 348. At this instant of clearance one of the pins 338 engages the pin 331 of the eccentric and starts to rotate the latter and the clutch member of which it is part whilethe follower moves in the groove 348. In so doing it, of course, follows the helical angle of the said groove and shifts the clutch still further to the left moving with it the yoke.34l

' into a release position (Fig. 12), where the trip lever 380 disengages the lug and is snapped by resilient member 383 to the front stop pin 382 and clear of the lug 310. The follower'moving in the cam groove as the clutch rotates then causes the clutch to shift toward the right'so that after a single revolution when said follower again abuts the shoulder 348, the clutch member has been so shifted that its pin 331v has disengaged the pins 338. Thus, a, single rotation only of the clutch member 328 occurs each time the trip lever engages the lug 310. The latter engagement occurs once for each revolution of section 3|0 of pulley wheel 308. Therefore, the speed of rotation of said wheel determines the frequency of single rotations of the clutch memof the pulley wheel 338.

her. In consequence. the frequency of the single ber roll 236 and the mandrel 2| 6.

its action and eliminates any irregularity in coil lengths. There is no danger of double tripping. Simple adjustment of the variable speed pulley 392 permits infinite change with the range of the variable speed device inv the length of coil cut-oif by changing the relative frequency of cut-off action as compared to the speed of coiling of the wire.

The coil formed on the mandrel and moved off the latter at its forward end passes through the tube 232 and is received by a guide 380. This guide 380 comprises an arm 38! suitably attached to'the frame H0. The upper portion 383 of this arm is provided with a semicircular groove 384 extending in the same direction as said mandrel 2H6 and concentric with respect to the axis of said mandrel. A semicircular tube 385 having lateral arms 386 is rotatably supported by these arms from a pivot spindle or rod 38'! carried by the vertical flange 230 and extending parallel to the groove 384. The concavity of tube 385 faces that of the groove 384 and the two function when in register as a tubular guide for the coiled wire passing thereto from the mandrel. Resilient means as a torsion spring 389 acting on the rod 381 and an arm 386 tend to maintain the tube 385 in registry with the groove 384.

When a length of coil is cut off from that being wound on the mandrel, it is desirable to effect quick removal thereof from the guide 380. To this end, a crank lever 390 is pivotally mounted on a pivot pin 39! carried by the vertical arm 230. One arm 390' of the lever extends into the path of travel of the connecting rod 323. The other arm 390 is connected by a linkage member 392 to a projecting lug 393 on one of the arms 386 supporting the tube 385. Thus, as the con- .necting rod reaches the top of its stroke, shown in dotted lines in Fig. 10, its upper edge engages the'arm 390' of lever 390 and rotates the latter to the dotted line position causing the linkage member 392 to rotate the arm 386 and tube 385 to the dotted position shown and permits the severed coil to fall from the groove 384. pact of the cut-off stroke of the blade is sumcient to dislodge the severed coil section from said groove. Spring 389 returns the tube 385 to full line position of the figure when the connecting rod returns to non-cutting-ofi position.

The guide 380 and its associated mechanism may be replaced by a simple receiving tray similar to the tray I80 of the first modification.

Operation of this modified form of machine, in brief, is as follows:

Wire 25? from the, spool 255 is led over the various pulleys 258, 259, 266, metering wheel 261, and thence to the bight between the lower rub- Then the shaft 212 and, consequently, the mandrel 2I6, are given a few manual rotations to start the wind on the mandrel. The rolls 235 and 236 are given the desired opposing biases with respect to each other and moved toward each other until they both press firmly on the wire-windings on the mandrel and are then clamped in this pasition. The machine is then started, causing the mandrel 2l6 to rotate at high speed. The

pand slightly and slide freely along the mandrel surface in axial direction toward the guide 888, passing off the mandrel in the tube 232 on the way to said guide. The lubricant applied (as described with respect to the first modification) to the face of the wire adjacent the face of the mandrel facilitates the sliding of the coil along the mandrel. .At intermittent periods controlled by the trip lever 360, as. hereinbefore described, the cut-ofi knife 320 sweeps across the exit end of tube 232 cutting off predetermined lengths of coil which fall from the opened guide 380 at the time of severance. The adjustable ratio of speed between the coiling speed of the mandrel and the rotational speed of the trip lever 368 on pulley section 3I8 determines the length of coil cut-oif. This ratio can be adjusted infinitely within the limits of the variable speed drive and with a high degree of accuracy to insure highly accurate cut-off of uniform predetermined lengths of coil.

In the embodiments shown, the rolls 235 and 236 have respectively the annular shoulders 235 and 236' at substantially the midpoints of their surface peripheries. by slightly reducing the diameter of the respective rolls on one Side of the respective shoulders The imcoefficient of friction between the mandrel and wind and forces the windings to move along the mandrel and clear of the rolls 235 and 236. Once clear of the rolls, the turns on the mandrel exfacilitate the guiding of the wire at the desired pitch angle during the coiling operation. The shoulder height depends upon tlie wire size and in cases of very small-sized wire can be eliminated. For the larger wire sizes, however, the shoulder is important.

The adjustability of the speed of drive of variquent readjustment of the machines during the preparation of a particular length of coil of a particular wire size.

The variable biasing of the rubber rolls permits the winding of differently pitched coils.

Various other advantages are inherent in thestructure described. It is to be understood, however, that variations in structural features within the scope of the appended claims may be inade without departing from the inventive ZigieaJ There is no intention of limitation tothe exact details of constructionshown and described.

I claim:

I. In a coilin'gmachine, means for. cutting oiT lengths of coil from the coil formed therein without impeding the coil forming operations comprising a severing member, periodic means for operating said severing member, and linkage means between-said severing member'and said operating means, said linkage means being so arranged as to provide a single cutting stroke and a single power return stroke of said severing member in one phase of operation of said periodic means and to maintain said severing member inactive during the entire return phase of operation of said operating means.

2. Ina coiling machine, means for cutting off lengths of coil from the coil formed therein without impeding the coil forming operations comprising a severing member, means for periodical- These shoulders producedly operating said severing member, linkage means between said severing member and said operating means, and means in conjunction with said linkage means for automatically changing the linkage ratios thereof during actuation of said linkage means so as to provide a single cutting stroke and a single power return stroke of said severing member in one phase of operation of said'periodic means and to maintain said severing member inactive during the entire return phase of operation of said operating means.

3. In a coiling machine, means for cutting off lengths of coil from the coil formed therein without impeding the coil forming operations comprising a severing member, means for periodically operating said severing member, said means having a going and a return stroke, linkage means between said severing member and said operating means and toggle controlled means in conjunction with said linkage means for changing automatically the linkage ratios of said linkage means during periods of the operation thereof so as to effect a single cutting strokeand single return stroke of said severing member for each going stroke of said operating means and serving to maintain said severing member inactive during the return stroke of said operating means. I

4. In a coiling machine, means for cutting off lengths of coil formed therein without impeding the coil forming operations comprising a severing member, electrically actuated means for periodically operating said severing member, linkage meansbetween said severing member and said operating means, means in conjunction with said linkage means for changing automatically the linkage ratios of said linkage means during periods of operation thereof, so as to effect a single cutting stroke and a single return stroke of said severing member for each periodic operation of saidoperating means, and means for electrically actuating said operating means periodically,

5. In a coiling machine, means for cutting off lengths of coil formed therein without impeding the coil forming operations comprising a severing member, a solenoid, a solenoid plunger reciprocally movable therein, linkage means connecting said solenoid plunger and said severing member, means in conjunction with said linkage means for changing automatically the linkage ratios of said linkage means during periods of movement of said plunger so as to effect a single cutting stroke and single return stroke of said severing member for each complete reciprocation of said plunger and means for periodically energizing said solenoid to effect each time a single complete reciprocation of said plunger.

6. In a coiling machine, means for cutting off v predetermined lengths of coil formed therein without impeding the coil forming operations comprising a severing member, a solenoid, a reciprocally movable solenoid operated member, linkage means connecting said last named member and said severing member, means in conjunction with said linkage means for changing automatically the linkage ratios of said linkage means during periods of movement of said solenoid operated member so as to efiect a single cutting stroke and single return stroke of said severing member for each complete reciprocation of said solenoid operated member, electrical switching means for introducing electrical power to energize said solenoid, and means for operating said electric switching means to efiect periodic energization and deenergization ofsaid solenoid.

7. In a coiling machine, means for severing lengths of coil from the coil formed therein without impeding the coil forming operations comprising a severing member mounted for reciprocal rotation at the coil emergingpoint of the ratio thereof being inefiective to impart movement to the severing member in the return direction of reciprocal movement of said reciprocally movable means, and means for automatically changing said linkage ratios from the first to the second thereof prior to the return move- -ment of said reciprocally movable means.

8. In a device as per claim '7, in which said automatic changing means comprises a locking member cooperating with said linkage means, and toggle means for automatically causing said locking member to engage and disengage said linkage means.

9. In a.coiling machine, a cut-off member, a reciprocally movable plunger for operating said cut-off member and linkage means connecting said plunger and said member, said linkage means comprising a link rotatably connected to said plunger, two other links rotatably connected to said link at a common point, one of said two other links being rotatably connected at another point thereof to said cut-off member and'the second of said two other links being rotatably mounted at another point thereof to a fixed center of rotation in said machine, and the connection between said first named link and said second of said two other links being variable along the lengthof said second of said two other links within limits, a locking member serving in one position to maintain one limiting relationship of.

said last named connection and in a second position to permit a second limiting relationship of said last named connection, and means for moving said locking member automatically intt. either of its said two positions.

10. In a coiling machine, meansfor cutting ofi lengths of coil from the coil formed therein without impeding the coil forming operation and means for automatically metering the length of each coil cut-off, saidlast named means includ-' ing electrically operated actuating means for moving said cut-off means into operative relat1onship with respect to said coil, a metering wheel over which the coil forming material passes prior to being formed into a coil to rotate said wheel, trip means operable during a prescribed period of rotation of said metering wheel for controlling the electric operation of said actuating means to cause operative movement of said cut-off means, and variable speed means interposed between said trip means and said metering wheel for varying the frequency of the operation of said trip means and said cut-oil means.

11. In a coiling machine, means for cutting off lengths of coil from the cofl formed therein without impeding the coil forming operations and means for automatically metering the and said metering wheel for varying the fre- 'quency, of the operation of said trip means and said cut-off means. j

12.,- In a'coiling machine, means for cutting vofflengths of coil from the coil formed therein without impeding the coil forming operation and means for automatically metering the length of each coil cut-oil", said last named means including a clutch means for operating said cut-oil? means, actuating means for driving said clutch means, a metering wheel over which the'coil forming material passes prior to being formed into a coil to rotate said wheel, and trip mechanism-operable during a prescribed period of the rotation of said metering wheel for moving said clutch means member into operative engage-' ment with said cut-off means.

13. In a coiling machine, a clutch member for operating cut-off means therein comprising a centric, a helical cam groove on'the periphery of said body for the reception of a dam follower,

said groove having a stop shoulder at its exit end and a passage connecting said exit end and the entry end of said groove, and a second groove on said periphery for the reception of means for moving said body along said shaft.

14. In a coiling machine having cut-off means, a clutch member for operating said cut-off means comprising a cylindrical body adapted to be borne on a rotatable shaft and having an eecentric at one end, a cam groove on the peripheral surface intermediate its ends for the recepcylindrical tubular body adapted to be borne 30' movably on a rotatable shaft and having an eon-- groove on its peripheral surface for the reception of a yoke member serving to move said body along said shaft as a unit, and engaging means at one end of said body adapted to engage removably with a member fixed to and driven by said shaft. I

15. In a coiling machine, means for cutting oil lengths of coil formed therein without irnpeding'thecoil forming operations comprising a severing member, power actuated means for periodically operatingsaid severing member, linkage means between said severing member and said operating means, means-in conjunction with said linkage means for changing automatically the linkage ratios of said linkage means during periods of operation thereof so as to effect a single cutting stroke and a single return stroke of said severing member for each periodicoperation of said operating means, and means for actuating said operating means periodically.

16. In a coiling machine, means for severing lengths of coil from the coil formed therein without impeding the coil forming operations comprising a severing member mounted for reciprocal movement adjacent the coil emerging point of the machine and adapted in its movement to sweep transversely across the path of movement of emerging coil, reciprocally movable means for so moving said severing member, linkage means connecting said severing member and said reciprocally movable means, said linkage means having variable linkage ratios, one ratio thereof being effective to impart a power cutting stroke and :a power return stroke to said severing member in one direction of reciprocal movement of said reciprocally movable means, and a second ratio thereof being ineffective to impart movement to the severing member in the return direction of. reciprocal movement of said reciprocally movable means, and means for automati'cally changing'said linkage ratios from one to the other during predetermined periods of movement of said reciprocally movable means.

' STEPHEN A. PLA'I'I'. 

